EP0777035A1 - Centrale combinée à chaudière à pressions multiples - Google Patents

Centrale combinée à chaudière à pressions multiples Download PDF

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Publication number
EP0777035A1
EP0777035A1 EP96810740A EP96810740A EP0777035A1 EP 0777035 A1 EP0777035 A1 EP 0777035A1 EP 96810740 A EP96810740 A EP 96810740A EP 96810740 A EP96810740 A EP 96810740A EP 0777035 A1 EP0777035 A1 EP 0777035A1
Authority
EP
European Patent Office
Prior art keywords
pressure
drum
low
separating bottle
evaporator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP96810740A
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German (de)
English (en)
Other versions
EP0777035B1 (fr
Inventor
Erhard Dr. Liebig
Christian Dr. Ruchti
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
General Electric Switzerland GmbH
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0777035A1 publication Critical patent/EP0777035A1/fr
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Publication of EP0777035B1 publication Critical patent/EP0777035B1/fr
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/106—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Definitions

  • the invention relates to a multi-pressure waste heat boiler with at least one circulation steam generator, consisting essentially of a low-pressure economizer, a low-pressure drum and a low-pressure evaporator and at least one forced-flow steam generator, essentially consisting of a high-pressure economizer, a high-pressure evaporator and a high-pressure superheater. It also relates to a method for operating such a system.
  • Such a gas-heated multi-pressure waste heat boiler is known from DE-A-41 26 631. It essentially consists of a circulation steam generator in the low pressure stage and a Benson evaporator in the medium pressure and high pressure stage.
  • the Benson evaporator of the high-pressure stage consists of two parts which are guided in cocurrent with the gas stream with differently converted heat. This should ensure stable flow conditions in the parallel tubes of the Benson evaporator.
  • the invention has for its object to provide a system of the type mentioned that allows the greatest possible flexibility in the driving style.
  • this is achieved in that the high-pressure economizer is fed from the steam drum of the circulation steam generator via a high-pressure feed pump, that a separating bottle is arranged between the high-pressure evaporator and the high-pressure superheater, and that the separating bottle is connected to the steam drum via a recirculation line.
  • a method for operating such a system is characterized in that when starting up until superheated conditions are reached at the outlet of the high-pressure evaporator, high-pressure saturated water is recirculated into the drum of the circulating steam generator via the separating bottle.
  • fresh air drawn in via a line 1 is compressed in a compressor 2 to the working pressure in the gas turbine system.
  • the compressed air is strongly heated in a combustion chamber 3, which is fired with natural gas, for example, and the fuel gas thus produced is expanded in a gas turbine 4 to perform work.
  • the energy obtained in this way is delivered to a generator 5 or the compressor 2.
  • the still hot exhaust gas from the gas turbine is fed via a line 6 from the outlet of the gas turbine to a heat recovery steam generator 7 and from there, after its heat has been given off, is passed outside via a line 8 and a chimney (not shown).
  • a multi-casing steam turbine 9, 10 and 11 is arranged on the same shaft with the gas turbine.
  • the working steam expanded in the low-pressure turbine 11 condenses in a condenser 13.
  • the condensate is conveyed directly into the steam generator 7 by means of a condensate pump 14. It is noteworthy that the system does not have any low-pressure preheaters, feed water tanks and high-pressure preheaters, which are usually heated by extraction steam.
  • the waste heat steam generation system 7 is designed as a standing boiler and in the present case works according to a two-pressure steam process. Of course, a horizontal boiler could also be used.
  • the low pressure system is designed as a circulation system with a drum, with a forced circulation system being selected here. It consists in the flue gas path of the boiler from a low-pressure economizer 15, into which the condensate is introduced, a low-pressure evaporator 16 and a low-pressure superheater 19.
  • the low-pressure evaporator is via a circulation pump 18 connected to a drum 17.
  • the superheated steam is transferred to a suitable stage of the medium-pressure steam turbine 10 via a low-pressure steam line 28.
  • the high-pressure system is designed as a once-through system and can therefore be designed for both subcritical and supercritical parameters. It essentially consists of the high-pressure economizer 21, the high-pressure evaporator 22 and the high-pressure superheater 23 in the flue gas path of the boiler.
  • the working medium is supplied to the high-pressure economizer 21 from the low-pressure drum 17 via a high-pressure feed pump 20. In this way, the feed water tank that has been customary up to now can be omitted.
  • the superheated steam is transferred to the high-pressure part 9 of the steam turbine via a live steam line 24.
  • a separation bottle 25 is provided for phase separation, into which the outlet of the high-pressure evaporator 22 opens.
  • the separator bottle is arranged at the same height as the low-pressure drum. It is connected to the high-pressure superheater 23 at its upper end. At its lower end, it is additionally provided with a drain pipe 29.
  • a further water line 31 branches off from this recirculation line and leads to the condenser 13.
  • a shut-off device 32 is also provided in this water line.
  • the steam is reheated before being transferred to the medium-pressure turbine 10.
  • This reheating takes place in the example in heat exchange surfaces 27 which are arranged in the flue gas path of the steam generator above the high-pressure superheater 23.
  • the low-pressure circulation system and the high-pressure continuous system are initially filled with water. Circulation in the low-pressure system is ensured via the circulation pump 18. Circulation in the high-pressure system via the separating bottle and the recirculation line 26 into the low-pressure drum is likewise ensured via the geodetic height, the pressure difference and the pumps.
  • the gas turbine is then started up. Their exhaust gases are fed into the steam generator and heat up the water circulating in the heat exchange surfaces.
  • the recirculation conducts heat from the high-pressure flow system into the drum of the low-pressure circulation system until superheated conditions are reached at the outlet of the high-pressure evaporator 22. This ensures that the heat is kept in the area of the boiler during start-up. Since there is no need to release heat to the environment via a cooling system, this procedure guarantees a very economical start-up.
  • the separator bottle ensures that the high-pressure superheater stays dry at all times and that superheated steam is available at the boiler outlet at an early stage. As soon as the pressure required for stable operation has been reached in the high-pressure evaporator, the live steam can be used to start the steam turbine in sliding pressure mode.
  • the time at which steam generation begins and the steam parameters such as pressure, temperature and mass flow can be influenced depending on the specific conditions of the system. This procedure guarantees a high degree of flexibility when starting off.
  • the regulation takes place exclusively via the speed-controlled feed pump, whereby the fresh steam temperature is set via the mass flow.
  • the feed pump can be operated at constant speed just as well with subsequent throttling of the feed water to the desired pressure.
  • the start-up procedure described is particularly suitable for warm starting the system.
  • the conditions are different for a cold start. It is important to prevent water and moisture breakthroughs to the turbine.
  • the feed water at least partially circulates around the feed pump 20 during a cold start.
  • saturated water evaporates when the pressure drops, which can lead to erosion and water hammer. This is remedied by the measure that the recirculation water is at least partially discharged until overheated conditions have been reached at the outlet of the high-pressure evaporator 22.
  • the water circulated from the separator bottle can, for example, be fed directly into the condenser 13 via the water line 31 or be discarded via the drain line 29. The latter will be carried out in particular on a cold start after a long standstill when there are doubts about the water quality.
  • the invention is not limited to the exemplary embodiment shown and described. Multi-pressure processes are also conceivable, with the pressure stages working in the forced pass being fed from the drums of the circulation systems. In deviation from the aforementioned forced circulation of the low pressure system, a natural circulation system can of course be used just as well. Furthermore, the invention is not tied to the presence of superheaters and reheaters. In deviation from the solutions described, according to which the geodetic height or the pressure difference are used for the recirculation from the separating bottle into the low-pressure drum, it may be appropriate to provide a separate circulation pump for this.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
EP96810740A 1995-11-28 1996-11-06 Procédé pour démarrer une chaudière à pressions multiples Expired - Lifetime EP0777035B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19544226 1995-11-28
DE19544226A DE19544226B4 (de) 1995-11-28 1995-11-28 Kombianlage mit Mehrdruckkessel
US08/747,405 US5765509A (en) 1995-11-28 1996-11-12 Combination plant with multi-pressure boiler

Publications (2)

Publication Number Publication Date
EP0777035A1 true EP0777035A1 (fr) 1997-06-04
EP0777035B1 EP0777035B1 (fr) 2003-07-09

Family

ID=26020724

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96810740A Expired - Lifetime EP0777035B1 (fr) 1995-11-28 1996-11-06 Procédé pour démarrer une chaudière à pressions multiples

Country Status (5)

Country Link
US (1) US5765509A (fr)
EP (1) EP0777035B1 (fr)
JP (1) JPH09170701A (fr)
CN (1) CN1130517C (fr)
DE (1) DE19544226B4 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0898054A1 (fr) * 1996-11-25 1999-02-24 Asea Brown Boveri AG Générateur de vapeur
EP0981014A1 (fr) * 1998-08-18 2000-02-23 Asea Brown Boveri AG Centrale d'énergie et procédé pour sa mise en marche et pour la purification de son cycle eau-vapeur
US8297236B2 (en) 2005-04-05 2012-10-30 Siemens Aktiengesellschaft Steam generator
EP3086033A1 (fr) * 2015-04-22 2016-10-26 Siemens Aktiengesellschaft Procédé et dispositif pour le démarrage d'un générateur de vapeur en continu

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19721854A1 (de) * 1997-05-26 1998-12-03 Asea Brown Boveri Verbesserung des Abscheidegrades von Dampfverunreinigungen in einem Dampf-Wasser-Separator
DE19736885A1 (de) * 1997-08-25 1999-03-04 Siemens Ag Dampferzeuger, insbesondere Abhitzedampferzeuger und Verfahren zum Betrieb dieses Dampferzeugers
DE59711190D1 (de) * 1997-11-19 2004-02-12 Alstom Switzerland Ltd Verfahren und Vorrichtung zur Brennstoffvorwärmung einer Feuerungsanlage
US6092490A (en) * 1998-04-03 2000-07-25 Combustion Engineering, Inc. Heat recovery steam generator
US5985883A (en) * 1998-09-25 1999-11-16 American Cyanamid Company Fungicidal trichlorophenyl-triazolopyrimidines
DE19846458C1 (de) * 1998-10-08 2000-03-30 Siemens Ag Verfahren zum Wiederanfahren einer Gas- und Dampfturbinenanlage
DE19849740A1 (de) * 1998-10-28 2000-01-05 Siemens Ag Gas- und Dampfturbinenanlage
DE19918347A1 (de) * 1999-04-22 2000-10-26 Asea Brown Boveri Verfahren und Vorrichtung zur schnellen Leistungssteigerung und Sicherstellung einer Zusatzleistung einer Gasturbinenanlage
DE10056128A1 (de) 2000-11-13 2002-06-06 Alstom Switzerland Ltd Verfahren zum Betreiben einer Gasturbinenanlage sowie eine dementsprechende Anlage
US7243619B2 (en) * 2004-10-20 2007-07-17 The Babcock & Wilcox Company Dual pressure recovery boiler
US8065815B2 (en) * 2006-10-10 2011-11-29 Rdp Technologies, Inc. Apparatus, method and system for treating sewage sludge
US8746184B2 (en) * 2010-01-28 2014-06-10 William P. Horne Steam boiler with radiants
CN102966941A (zh) * 2012-11-26 2013-03-13 杭州国电机械设计研究院有限公司 一种相变换热器与低压省煤器联合的余热回收系统
US10180086B2 (en) * 2013-09-26 2019-01-15 Nooter/Eriksen, Inc. Heat exchanging system and method for a heat recovery steam generator
KR20240093200A (ko) * 2022-12-15 2024-06-24 두산에너빌리티 주식회사 수직 관류형 배열회수 보일러 및 이를 포함하는 복합발전 시스템

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0359735A1 (fr) * 1988-09-14 1990-03-21 AUSTRIAN ENERGY & ENVIRONMENT SGP/WAAGNER-BIRO GmbH Chaudière de récupération
DE4126631A1 (de) 1991-08-12 1993-02-18 Siemens Ag Gasbeheizter abhitzedampferzeuger
EP0561220A1 (fr) * 1992-03-16 1993-09-22 Siemens Aktiengesellschaft Procédé pour le fonctionnement d'une installation de génération de vapeur et générateur de vapeur

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DE1041973B (de) * 1956-11-22 1958-10-30 Sulzer Ag Dampfkraftanlage
DE1209811B (de) * 1961-03-30 1966-01-27 Bbc Brown Boveri & Cie Kombinierte Gasturbinen-Dampfkraft-Anlage
US3370573A (en) * 1966-12-12 1968-02-27 Combustion Eng Start-up system for combined circulation steam generator
CH477651A (de) * 1967-07-13 1969-08-31 Sulzer Ag Hochdruck-Zwangdurchlaufdampferzeugeranlage mit aus gasdicht geschweissten Rohren bestehender Brennkammer und Verfahren zum Betrieb der Anlage
GB1311869A (en) * 1969-12-12 1973-03-28 Foster Wheeler Brown Boilers Steam boilers
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US3841270A (en) * 1972-11-01 1974-10-15 Westinghouse Electric Corp Flow restrictor for an evaporator
CH632331A5 (de) * 1978-10-03 1982-09-30 Sulzer Ag Verfahren zum anfahren eines zwanglaufdampferzeugers.
DE3447265A1 (de) * 1984-12-22 1986-06-26 L. & C. Steinmüller GmbH, 5270 Gummersbach Verfahren und vorrichtung zur erzeugung von hochgespanntem und ueberhitztem dampf
US4854121A (en) * 1986-10-09 1989-08-08 Kabushiki Kaisha Toshiba Combined cycle power plant capable of controlling water level in boiler drum of power plant
DE3741882C1 (en) * 1987-12-10 1989-02-02 Gea Luftkuehler Happel Gmbh Steam generator with once-through forced flow
DE3804605A1 (de) * 1988-02-12 1989-08-24 Siemens Ag Verfahren und anlage zur abhitzedampferzeugung
DE58909259D1 (de) * 1989-10-30 1995-06-29 Siemens Ag Durchlaufdampferzeuger.
JPH05240402A (ja) * 1992-03-27 1993-09-17 Babcock Hitachi Kk 廃熱回収ボイラの運転方法
US5267434A (en) * 1992-04-14 1993-12-07 Siemens Power Corporation Gas turbine topped steam plant
EP0579061A1 (fr) * 1992-07-15 1994-01-19 Siemens Aktiengesellschaft Méthode de fonctionnement d'un système à turbines à gaz et à vapeur et système pour la mise en oeuvre de la méthode
DE4321081A1 (de) * 1993-06-24 1995-01-05 Siemens Ag Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage sowie danach arbeitende GuD-Anlage
JPH07119906A (ja) * 1993-10-28 1995-05-12 Ishikawajima Harima Heavy Ind Co Ltd ボイラの補助蒸気自動切換装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0359735A1 (fr) * 1988-09-14 1990-03-21 AUSTRIAN ENERGY & ENVIRONMENT SGP/WAAGNER-BIRO GmbH Chaudière de récupération
DE4126631A1 (de) 1991-08-12 1993-02-18 Siemens Ag Gasbeheizter abhitzedampferzeuger
EP0561220A1 (fr) * 1992-03-16 1993-09-22 Siemens Aktiengesellschaft Procédé pour le fonctionnement d'une installation de génération de vapeur et générateur de vapeur

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0898054A1 (fr) * 1996-11-25 1999-02-24 Asea Brown Boveri AG Générateur de vapeur
EP0981014A1 (fr) * 1998-08-18 2000-02-23 Asea Brown Boveri AG Centrale d'énergie et procédé pour sa mise en marche et pour la purification de son cycle eau-vapeur
US6155054A (en) * 1998-08-18 2000-12-05 Asea Brown Boveri Ag Steam power plant and method of and cleaning its steam/water cycle
US8297236B2 (en) 2005-04-05 2012-10-30 Siemens Aktiengesellschaft Steam generator
EP3086033A1 (fr) * 2015-04-22 2016-10-26 Siemens Aktiengesellschaft Procédé et dispositif pour le démarrage d'un générateur de vapeur en continu

Also Published As

Publication number Publication date
EP0777035B1 (fr) 2003-07-09
DE19544226B4 (de) 2007-03-29
US5765509A (en) 1998-06-16
JPH09170701A (ja) 1997-06-30
DE19544226A1 (de) 1997-06-05
CN1165267A (zh) 1997-11-19
CN1130517C (zh) 2003-12-10

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